Compressor and air conditioner

Abstract

A compressor and an air conditioner. The compressor comprises a first housing (11), a compression mechanism (14), a sensor (510), and a vibration exciter (520). The compression mechanism (14) is disposed within the first housing (11) and is configured to compress a refrigerant. The sensor (510) is disposed on the circumferential wall of the first housing (11) and is configured to acquire a first tangential vibration signal of the first housing (11). The vibration exciter (520) is disposed on the circumferential wall of the first housing (11) and is configured, on the basis of the first tangential vibration signal acquired by the sensor (510), to send a second signal having an equal amplitude and opposite phase, so as to reduce the vibration of the compressor.

Description

Compressor and air conditioner

[0001] This application claims priority to Chinese Patent Application No. 202421546117.5, filed on July 02, 2024; Chinese Patent Application No. 202421546465.2, filed on July 02, 2024; Chinese Patent Application No. 202421546064.7, filed on July 02, 2024; Chinese Patent Application No. 202421546514.2, filed on July 02, 2024; Chinese Patent Application No. 202421546201.7, filed on July 02, 2024; Chinese Patent Application No. 202421546166.9, filed on July 02, 2024; Chinese Patent Application No. 202421546573.X, filed on July 02, 2024; and Chinese Patent Application No. 202421546550.9, filed on July 02, 2024, the contents of all of which are incorporated by reference in their entirety. TECHNICAL FIELD

[0002] The present disclosure relates to the field of air conditioning technology, and in particular, to a compressor and an air conditioner. BACKGROUND

[0003] An air conditioner performs a refrigeration and heating cycle of the air conditioner by using a compressor, a condenser, an expansion valve, and an evaporator. A scroll rotor compressor generally includes a housing, a motor, and a compression mechanism disposed in the housing. In a double-cylinder rotor compressor, a second sub-silencer, a second bearing, a second cylinder, a middle partition plate, a first cylinder, a first bearing, a first sub-silencer, and a motor are sequentially disposed from bottom to top on an eccentric crankshaft, a second piston is disposed in the second cylinder, and a first piston is disposed in the first cylinder.

[0004] SUMMARY

[0005] In one aspect, a compressor is provided, including a first housing, a compression mechanism, a sensor, and an exciter. The compression mechanism is disposed in the first housing, and is configured to compress refrigerant. The sensor is disposed on a circumferential wall of the first housing, and is configured to acquire a tangential vibration first signal of the first housing. The exciter is disposed on the circumferential wall of the first housing, and is configured to emit a second signal with equal amplitude and opposite phase according to the tangential vibration first signal acquired by the sensor, so as to reduce vibration of the compressor.

[0006] In another aspect, an air conditioner is provided, which includes an indoor unit and an outdoor unit. The outdoor unit is connected to the indoor unit. The indoor unit includes a first heat exchanger and a fan assembly. The first heat exchanger is located in the indoor unit and is configured to exchange heat with indoor air. The fan assembly is located in the indoor unit and is configured to output the indoor air after heat exchange to the indoor. The outdoor unit includes a second heat exchanger and a compressor. The second heat exchanger is configured to exchange heat with outdoor air. The compressor is the compressor described above. BRIEF DESCRIPTION OF DRAWINGS

[0007] FIG. 1A is a structural diagram of a compressor according to some embodiments;

[0008] FIG. IB is a partial view of FIG. 1A;

[0009] FIG. 1C is another structural diagram of a compressor according to some embodiments;

[0010] FIG. 2A is a schematic diagram of a compressor according to some embodiments;

[0011] FIG. 2B is a schematic block diagram of a processor, a sensor, and an exciter according to some embodiments;

[0012] FIG. 3 is a sectional view of a compressor body according to some embodiments;

[0013] FIG. 4 is a sectional view of a compressor mechanism according to some embodiments;

[0014] FIG. 5 is a partial enlarged view of circle A in FIG. 4;

[0015] FIG. 6 is a sectional view of an eccentric crankshaft, a first bearing, and a rotor according to some embodiments;

[0016] FIG. 7 is a partial view of a first shaft section of an eccentric crankshaft and a rotor according to some embodiments;

[0017] FIG. 8 is a sectional view of an eccentric crankshaft and a first bearing according to some embodiments;

[0018] FIG. 9 is a sectional view of a first bearing according to some embodiments;

[0019] FIG. 10 is a structural diagram of an eccentric crankshaft according to some embodiments;

[0020] FIG. 11 is a sectional view of an eccentric crankshaft according to some embodiments;

[0021] FIG. 12A is another sectional view of an eccentric crankshaft according to some embodiments;

[0022] FIG. 12B is a partial enlarged view of circle B in FIG. 12A.

[0023] Figure 13 is a structural diagram of a passage piece and a moving piece according to some embodiments;

[0024] Figure 14 is another structural diagram of a passage piece and a moving piece according to some embodiments;

[0025] Figure 15 is a structural diagram of a stator according to some embodiments;

[0026] Figure 16 is a top view of a compressor according to some embodiments;

[0027] Figure 17 is a structural diagram of a bracket according to some embodiments;

[0028] Figure 18 is another structural diagram of a bracket according to some embodiments;

[0029] Figure 19 is a top view of another compressor according to some embodiments;

[0030] Figure 20 is a structural diagram of another bracket according to some embodiments;

[0031] Figure 21 is a data plot of initial oiling time of a compressor according to some embodiments;

[0032] Figure 22 is a data plot of oil discharge rate of a compressor according to some embodiments;

[0033] Figure 23 is a plot of (D7-D6) / D5 vs. first bearing friction loss according to some embodiments;

[0034] Figure 24 is a plot of (D7-D6) / H3 vs. first bearing radial deformation according to some embodiments;

[0035] Figure 25 is a plot of D5 / D11 x H5 / H4 vs. compressor friction loss according to some embodiments;

[0036] Figure 26 is a plot of H5 / H6 x D5 / D11 vs. first bearing radial deformation according to some embodiments;

[0037] Figure 27 is a plot of H7 / H2 vs. compressor COP efficiency according to some embodiments;

[0038] Figure 28 is a plot of (H8+H5) / H9 vs. first bearing radial deformation according to some embodiments;

[0039] Figure 29 is a plot of (D8-D9) / (H9-H8) vs. motor efficiency, first bearing radial deformation according to some embodiments;

[0040] FIG. 30 is a graph of (D11-D5) / H5 vs. first bearing radial deformation according to some embodiments;

[0041] FIG. 31 is a graph of D9 / D5 vs. motor efficiency according to some embodiments;

[0042] FIG. 32 is a graph of D8 / D9 vs. motor efficiency according to some embodiments;

[0043] FIG. 33 is a graph of H11 / (H10xH8) vs. motor efficiency according to some embodiments;

[0044] FIG. 34 is a graph of D14 / (H8xD9) vs. compressor noise, motor efficiency according to some embodiments;

[0045] FIG. 35 is a graph of H16 / (H8xS) vs. motor noise, efficiency according to some embodiments;

[0046] FIG. 36 is a graph of d1 / d2 vs. motor efficiency, speed according to some embodiments;

[0047] FIG. 37 is a graph of d4 / S vs. motor efficiency, eccentric crankshaft deformation according to some embodiments. DETAILED DESCRIPTION

[0048] Some embodiments of the present disclosure will be described hereinafter with reference to the accompanying drawings, in which specific embodiments are shown. It is to be understood that the present disclosure is not limited to the specific embodiments described herein, but encompasses numerous other embodiments, which are within the scope of the present disclosure. The present disclosure is directed to all such modifications and variants of the embodiments disclosed herein.

[0049] Unless the context clearly requires otherwise, throughout the description and the claims, the term "comprise," and variations thereof (e.g., "comprises" and "comprising"), will be construed to be inclusive in a manner consistent with the term's plain meaning, namely, "including but not limited to." In describing the description, the terms "one embodiment," "some embodiments," "exemplary embodiments," "example," "specific example" or "some examples," and the like, mean that a particular feature, structure, material, or characteristic is included in at least one embodiment or example of the disclosure, but that it can not be included in other embodiments or examples. The illustrative appearance of the foregoing terms in various places in the description are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics can be combined in any suitable manner in one or more embodiments or examples.

[0050] Hereinafter, the terms "first", "second", etc. are used only for the purpose of description and should not be construed as indicating or implying relative importance or implying the number of the technical features indicated. Therefore, the features defined with "first", "second" can explicitly or implicitly include one or more of the features. In the description of the embodiments of the disclosure, the meaning of "a plurality of" is two or more, unless otherwise specified.

[0051] In describing some embodiments, "coupled" and "connected," and variations thereof, can be used. The term "connected" should be interpreted broadly, for example, "connected" can be fixedly connected, or detachably connected, or integrated; can be directly connected, or indirectly connected through an intermediate medium. The term "coupled" indicates that two or more components have direct physical contact or electrical contact. The term "coupled" or "communicatively coupled" can also mean that two or more components do not have direct contact with each other, but still cooperate or interact with each other. The embodiments disclosed herein are not necessarily limited to the content herein.

[0052] "A, B, and C at least one of" has the same meaning as "at least one of A, B, or C", and includes the following combinations of A, B, and C: only A, only B, only C, a combination of A and B, a combination of A and C, a combination of B and C, and a combination of A, B, and C.

[0053] "A and / or B" includes the following three combinations: only A, only B, and a combination of A and B.

[0054] The use of “adapted for” or “configured for” herein means open and inclusive language that does not exclude devices adapted for or configured for performing additional tasks or steps.

[0055] As used herein, “about,” “approximately” or “around” includes the recited value and the average value within an acceptable range of deviation from the particular value, as determined by one of ordinary skill in the art taking into account the measurement being discussed and the error associated with the measurement of the particular quantity (i.e., the limitations of the measurement system).

[0056] As used herein, “parallel,” “perpendicular,” “equal” includes the recited condition and conditions that approximate the recited condition, the approximation being within an acceptable range of deviation, as determined by one of ordinary skill in the art taking into account the measurement being discussed and the error associated with the measurement of the particular quantity (i.e., the limitations of the measurement system). For example, “parallel” includes absolute parallel and near parallel, where the acceptable range of deviation for near parallel can be, for example, within 5°; “perpendicular” includes absolute perpendicular and near perpendicular, where the acceptable range of deviation for near perpendicular can also be, for example, within 5°. “Equal” includes absolute equality and near equality, where the acceptable range of deviation for near equality can be, for example, a difference between the two that is less than or equal to 5% of either.

[0057] [Air Conditioner]

[0058] An air conditioner in some embodiments of the present disclosure performs a refrigeration and heating cycle of the air conditioner by using a compressor, a condenser, an expansion valve, and an evaporator. The refrigeration and heating cycle includes a series of processes involving compression, condensation, expansion, and evaporation, and performs refrigeration or heating for an indoor space.

[0059] A low-temperature and low-pressure refrigerant enters the compressor, which compresses the refrigerant gas into a high-temperature and high-pressure state and discharges the compressed refrigerant gas. The discharged refrigerant gas flows into the condenser. The condenser condenses the compressed refrigerant into a liquid phase, and heat is released to the surrounding environment through the condensation process.

[0060] The expansion valve expands the high-temperature and high-pressure state liquid phase refrigerant formed in the condenser into a low-pressure liquid phase refrigerant. The evaporator evaporates the refrigerant expanded in the expansion valve and returns the refrigerant gas in a low-temperature and low-pressure state to the compressor. The evaporator can achieve a refrigeration effect by exchanging heat with a material to be cooled using the latent heat of evaporation of the refrigerant. Throughout the cycle, the air conditioner can adjust the temperature of the indoor space.

[0061] The outdoor unit of an air conditioner refers to the part of the refrigeration cycle including the compressor and the outdoor heat exchanger, and the indoor unit of the air conditioner includes the indoor heat exchanger, and the expansion valve can be provided in the indoor unit or the outdoor unit.

[0062] The indoor heat exchanger and the outdoor heat exchanger are used as a condenser or an evaporator. When the indoor heat exchanger is used as a condenser, the air conditioner performs a heating mode; when the indoor heat exchanger is used as an evaporator, the air conditioner performs a cooling mode.

[0063] It should be noted that the first heat exchanger (such as the indoor heat exchanger) is configured to exchange heat with indoor air. The second heat exchanger (such as the outdoor heat exchanger) is configured to exchange heat with indoor air.

[0064] In some embodiments, the indoor unit further includes a fan assembly located in the indoor unit, and the fan assembly is configured to output the heat-exchanged indoor air to the indoor.

[0065] The outdoor unit further includes a four-way valve configured to switch the indoor heat exchanger and the outdoor heat exchanger as a condenser or an evaporator. The working principle of the air conditioner in the cooling mode is that the compressor works to make the indoor heat exchanger (in the indoor unit, which is an evaporator at this time) in an ultra-low pressure state, the liquid refrigerant in the indoor heat exchanger evaporates rapidly to absorb heat, the wind blown by the indoor fan becomes cold wind after being cooled by the indoor heat exchanger coil, and the cold wind is blown into the indoor, the evaporated refrigerant is pressurized by the compressor, and then condensed into liquid in the high-pressure environment of the outdoor heat exchanger (in the outdoor unit, which is a condenser at this time), and releases heat, which is dissipated to the atmosphere by the outdoor fan, so that the cooling effect is achieved through the cycle.

[0066] The working principle of the air conditioner in the heating mode is that the gaseous refrigerant is pressurized by the compressor to become a high-temperature and high-pressure gas, enters the indoor heat exchanger (which is a condenser at this time), condenses and releases heat to become a liquid, and at the same time heats the indoor air, so as to achieve the purpose of increasing the indoor temperature. The liquid refrigerant is reduced in pressure by the throttling device, enters the outdoor heat exchanger (which is an evaporator at this time), evaporates and absorbs heat to become a gas, and at the same time absorbs the heat of the outdoor air (the outdoor air becomes colder), becomes gaseous refrigerant, and enters the compressor again to start the next cycle.

[0067] [Compressor body]

[0068] The compressor in some embodiments of the present disclosure is a rolling rotor type compressor, referring to FIG. 1A and FIG. 3, the compressor includes a compressor body 1. The compressor body 1 includes a first shell 11, and an enclosed inner cavity is formed in the first shell 11.

[0069] The compressor body 1 includes a motor 13 arranged in the inner cavity.

[0070] In some embodiments, referring to FIG. 4, the compressor body 1 comprises a compression mechanism 14, which is arranged in the inner cavity of the first shell 11.

[0071] The motor 13 provides power for the compression mechanism 14. The compression mechanism 14 is configured to compress refrigerant. The motor 13 is arranged above the compression mechanism 14. FIG. 4 is a schematic diagram of one structure of the compression mechanism 14.

[0072] The first shell 11 comprises an upper shell, a circumferential shell, and a lower shell. The circumferential shell is arranged between the upper shell and the lower shell. The upper shell is arranged at the top of the circumferential shell, and the lower shell is arranged at the bottom of the circumferential shell. The upper shell, the circumferential shell, and the lower shell enclose the inner cavity of the compressor body 1.

[0073] In some embodiments, referring to FIG. 3, the motor 13 comprises a stator 310 and a rotor 320. The stator 310 is fixedly connected with the inner wall of the first shell 11 to achieve fixed installation of the motor 13 in the compressor inner cavity. FIG. 15 is a structure diagram of the stator 310.

[0074] In some embodiments, referring to FIG. 4, the compression mechanism 14 comprises an eccentric crankshaft 110, a cylinder, a piston, a bearing, a muffler, etc.

[0075] In some embodiments, referring to FIGS. 10 and 11, the eccentric crankshaft 110 comprises a first shaft segment 111, an eccentric shaft segment, and a second shaft segment 115. The first shaft segment 111 is fixedly connected with the rotor 320. The compression cavity of the cylinder is provided with a piston, which is sleeved on the eccentric shaft segment. The bearing is fixedly connected with the cylinder, and the bearing is provided with a bearing exhaust hole, which is in communication with the compression cavity. The cylinder is provided with a slide vane groove, and the slide vane groove is provided with a slide vane. The eccentric crankshaft 110 drives the piston to make a circumferential motion in the compression cavity, and the slide vane reciprocates along the slide vane groove. The slide vane is always in abutment with the piston, and the slide vane and the piston divide the compression cavity into a high-pressure cavity and a low-pressure cavity.

[0076] The working principle of the compressor is as follows: the stator 310 of the motor 13 generates a magnetic pull after being energized. The rotor 320 of the motor 13 rotates under the action of the magnetic pull of the stator and drives the eccentric crankshaft 110 to rotate together. The rotation of the eccentric crankshaft 110 drives the piston sleeved on the eccentric shaft segment to make an eccentric circumferential motion in the compression cavity of the cylinder. The slide vane reciprocates in the slide vane groove. The slide vane and the piston divide the compression cavity of the cylinder into a high-pressure cavity and a low-pressure cavity. The eccentric crankshaft 110 drives the piston to rotate one circle to complete a suction from the low-pressure cavity and a discharge from the high-pressure cavity, thereby realizing the compression of the compressor on the gas. The compressed gas is discharged through the bearing exhaust hole.

[0077] In some embodiments, the compressor body 1 is a double-cylinder rolling rotor type, referring to FIGS. 3 and 4, the compressor mechanism 14 includes an eccentric crankshaft 110, two cylinders (a first cylinder 122 and a second cylinder 121, respectively), two bearings (a first bearing 152 and a second bearing 151, respectively), two pistons (a first piston 132 and a second piston 131, respectively), a partition plate 160, and two mufflers 800 (a first sub-muffler 142 and a second sub-muffler 141, respectively).

[0078] Referring to FIGS. 10 and 11, the eccentric crankshaft 110 includes, from top to bottom, a first shaft segment 111, a first eccentric shaft segment 112, a connecting shaft segment 113, a second eccentric shaft segment 114, and a second shaft segment 115; the first cylinder 122 is provided with the first piston 132 capable of eccentric motion in a compression chamber of the first cylinder 122, and the first piston 132 is sleeved on the first eccentric shaft segment 112; the second cylinder 121 is provided with the second piston 131 capable of eccentric motion in a compression chamber of the second cylinder 121, and the second piston 131 is sleeved on the second eccentric shaft segment 114; the partition plate 160 is sleeved on the connecting shaft segment 113, and the partition plate 160 is located between the first cylinder 122 and the second cylinder 121; the first bearing 152 (an upper bearing) is sleeved on the first shaft segment 111 and connected with the first cylinder 122 at the same time; and the second bearing 151 (a lower bearing) is sleeved on the second shaft segment 115 and connected with the second cylinder 121 at the same time.

[0079] The first eccentric shaft segment 112 and the second eccentric shaft segment 114 are arranged at a relative angle of 180°, the first piston 132 and the second piston 131 simultaneously perform eccentric rotation, compressed gas in the compression chamber of the first cylinder 122 is discharged through the exhaust hole on the first bearing 152, and compressed gas in the compression chamber of the second cylinder 121 is discharged through the exhaust hole on the second bearing 151.

[0080] The first sub-muffler 142 is arranged on the first bearing 152, the first sub-muffler 142 covers the exhaust hole of the first bearing 152, compressed gas in the first cylinder 122 is first discharged to the space surrounded by the first sub-muffler 142 and the first bearing 152 through the exhaust hole of the first bearing 152, and then discharged to the inner cavity of the compressor through the exhaust hole of the upper muffler 142.

[0081] The second sub-muffler 141 is arranged on the second bearing 151, the second sub-muffler 141 covers the exhaust hole of the second bearing 151, and compressed gas in the second cylinder 121 is first discharged to the space surrounded by the second sub-muffler 141 and the second bearing 151 through the exhaust hole of the second bearing 151.

[0082] In some embodiments, unlike the related art, no exhaust hole is provided on the second sub-silencer 141 in FIG. 4, and a plurality of up-and-down airflow passages 170 are provided on the walls of the first bearing 152, the first cylinder 122, the middle plate 160, the second cylinder 121, and the second bearing 151. The second bearing 151 discharges the compressed gas in the second sub-silencer 141 upward to the space surrounded by the first bearing 152 and the first sub-silencer 142 through the airflow passages 170, and then discharges the compressed gas to the inner cavity of the compressor through the exhaust hole of the first sub-silencer 142.

[0083] [Gas-liquid separator]

[0084] In some embodiments, referring to FIGS. 1A and 2A, the compressor includes a gas-liquid separator 2 provided outside the compressor body 1 and configured to provide gaseous refrigerant into the compression chamber of the compression mechanism 14. The gas-liquid separator 2 separates the liquid refrigerant from the gaseous refrigerant to prevent the liquid refrigerant from entering the compression chamber of the compressor body 1 and causing the compressor to malfunction.

[0085] The gas-liquid separator 2 includes a second housing 21, and an outlet pipe 22 is provided at the bottom of the second housing 21. One end of the outlet pipe 22 extends into the inner cavity of the second housing 21, and the other end of the outlet pipe 22 is connected to the compression mechanism 14 to provide gaseous refrigerant to the compression mechanism 14.

[0086] [Structure of first bearing and motor]

[0087] In some embodiments, the first bearing 152 and the motor 13 are sleeved on the first shaft segment 111 of the eccentric crankshaft 110, and the motor 13 is located above the first bearing 152. The size ratio relationship between the first bearing 152 and the motor 13 will directly affect the radial deformation and wear of the first bearing 152, thereby affecting the performance of the compressor.

[0088] Therefore, in some embodiments of the present disclosure, the size ratio relationship between the first bearing 152 and the motor 13 is optimized to reduce the wear of the first bearing 152 and improve the performance of the compressor.

[0089] For example, referring to FIG. 9, the height distance between the welding point of the first sub-bearing 1521 (lateral part) of the first bearing 152 and the top end of the first bearing 152 is H5, and the outer diameter of the first sub-bearing 1521 of the first bearing 152 is D8. Referring to FIGS. 3, 6, and 7, the motor 13 includes a rotor 320 and a stator 310, the rotor 320 is sleeved on the first shaft segment 111, the height of the rotor 320 along the axial direction of the eccentric crankshaft 110 is H8, the height distance between the top end of the rotor 320 and the welding point of the first sub-bearing 1521 is H9, and the outer diameter of the rotor 320 is D9.

[0090] It should be noted that when (H8+H5) / H9>0.9, the first bearing 152 has small radial deformation and small stress in this range, which is conducive to reducing wear and improving the reliability of the first bearing 152. FIG. 28 shows a graph of (H8+H5) / H9 and the radial deformation of the first bearing 152.

[0091] It should be noted that when (D8-D9) / (H9-H8)∈[1, 1.5], the motor has high efficiency, and the first bearing 152 has small radial deformation and small stress in this range, which is conducive to reducing wear and improving the reliability of the first bearing 152. The upward convex arc-shaped curve in FIG. 29 is a graph of (D8-D9) / (H9-H8) and the motor efficiency, and the downward concave arc-shaped curve is a graph of (D8-D9) / (H9-H8) and the radial deformation of the first bearing 152.

[0092] In some embodiments, referring to FIG. 9, the outer diameter of the shaft shoulder of the second sub-bearing 1522 (vertical part) is D11, the height distance between the welding point of the first sub-bearing 1521 and the top end of the first bearing 152 is H5, referring to FIG. 11, the outer diameter of the first shaft segment 111 is D5, and (D11-D5) / H5∈[0.1, 0.3], in which range the first bearing 152 has good radial deformation, small stress, and is conducive to reducing wear and improving the reliability of the first bearing 152. FIG. 30 shows a graph of (D11-D5) / H5 and the radial deformation of the first bearing 152.

[0093] In some embodiments, referring to FIG. 6, the outer diameter of the rotor 320 is D9, referring to FIG. 11, the outer diameter of the first shaft segment 111 is D5, and D9 / D5∈[2.5, 4], in which range the motor has high efficiency. FIG. 31 shows a graph of D9 / D5 and the motor efficiency.

[0094] In some embodiments, referring to FIG. 9, the outer diameter of the first sub-bearing 1521 is D8. Referring to FIG. 6, the outer diameter of the rotor 320 is D9, and D8 / D9∈[1.2, 2], in which range the motor has high efficiency. FIG. 32 shows a graph of D8 / D9 and the motor efficiency.

[0095] In some embodiments, the motor 13 and the first bearing 152 are arranged on the first shaft segment 111, and the motor 13 is located above the first bearing 152. The bottom of the rotor 320 of the motor 13 is provided with a counterbore 321, the first shaft segment 111 passes through the counterbore 321, and the top of the second sub-bearing 1522 of the first bearing 152 extends into the counterbore 321 to avoid interference between the first bearing 152 and the motor 13. If the height of the counterbore 321 is too low, it will interfere with the first bearing 152; if the height of the counterbore 321 is too high, it will cause the compressor efficiency to decrease.

[0096] Based on this, in some embodiments of the present disclosure, by optimizing the design of the counterbore 321 on the rotor 320, not only can the motor 13 interfere with the first bearing 152 be avoided, but also the high efficiency of the motor 13 can be ensured.

[0097] For example, referring to FIG. 7, the height of the counterbore 321 is H10, the height distance of the second sub-bearing 1522 extending into the counterbore 321 is H11, the height of the rotor 320 is H8, and 0.006 < H11 / (H10 x H8) < 0.009. Within this range, the efficiency of the motor 13 can be improved. FIG. 33 shows a graph of H11 / (H10 x H8) and motor efficiency.

[0098] [Structure of the first bearing]

[0099] In some embodiments, referring to FIGS. 8 and 9, the first bearing 152 is sleeved on the first shaft segment 111. The first bearing 152 includes a one-piece structure of the first sub-bearing 1521 and the second sub-bearing 1522, and the first sub-bearing 1521 is arranged at the bottom of the second sub-bearing 1522. The second sub-bearing 1522 is provided with a through shaft hole, and the first shaft segment 111 is arranged in the shaft hole of the second sub-bearing 1522. The first sub-bearing 1521 is provided with an annular groove 1523 with an open bottom, and the annular groove 1523 surrounds the first shaft segment 111, that is, the annular groove 1523 surrounds the shaft hole of the first bearing 152.

[0100] By arranging the annular groove 1523, the contact between the first bearing 152 and the eccentric crankshaft 110 is surface contact, so as to improve the wear. The proportional relationship between the arrangement height, inner diameter and other dimensions of the annular groove 1523 and the diameter and other dimensions of the eccentric crankshaft 110 will affect the radial deformation and wear of the first bearing 152, thereby affecting the performance of the compressor.

[0101] Based on this, in some embodiments of the present disclosure, the proportional relationship between the arrangement height, inner diameter and other dimensions of the annular groove 1523 and the diameter and other dimensions of the eccentric crankshaft 110 is optimized to reduce the wear of the first bearing 152 and improve the performance of the compressor.

[0102] For example, referring to FIG. 11, the diameter of the first shaft segment 111 of the eccentric crankshaft 110 is D5. Referring to FIG. 9, the height of the annular groove 1523 is H3, the inner diameter of the annular groove 1523 is D6, and the outer diameter of the annular groove 1523 is D7.

[0103] It should be noted that (D7-D6) / D5 ∈ [0.09, 0.13], and within this range, the friction loss of the first bearing 152 is small. FIG. 23 shows a graph of (D7-D6) / D5 and the friction loss of the first bearing 152.

[0104] It should be noted that (D7-D6) / H3∈[0.2, 0.6], in this range, the first bearing 152 has small radial deformation and small stress, which is beneficial to reduce wear and improve the reliability of the first bearing 152. FIG. 24 shows a relationship diagram of (D7-D6) / H3 and the radial deformation of the first bearing 152.

[0105] In some embodiments, referring to FIG. 9, the outer diameter of the shaft shoulder of the second sub-bearing 1522 is D11. The second sub-bearing 1522 has a multi-section stepped structure, and the outer diameter of the second sub-bearing 1522 gradually increases from top to bottom. The outer diameter D11 of the shaft shoulder is the outer diameter of the upper section of the second sub-bearing 1522.

[0106] The height of the first bearing 152 is H4, that is, the distance between the top end of the second sub-bearing 1522 and the bottom end of the first sub-bearing 1521.

[0107] The first bearing 152 is welded to the inner wall of the first shell 11 of the compressor, and the height distance between the welding point of the first bearing 152 and the top end of the second sub-bearing 1522 is H5. For example, the circumferential outer wall of the first sub-bearing 1521 is welded to the circumferential inner wall of the first shell 11.

[0108] It should be noted that when D5 / D11×H5 / H4>0.45, in this range, the compressor has small friction loss. FIG. 25 shows a relationship diagram of D5 / D11×H5 / H4 and the friction loss of the compressor.

[0109] In some embodiments, referring to FIG. 9, the first bearing 152 is welded to the inner wall of the first shell 11, and the height distance between the welding point of the first bearing 152 and the top end of the second sub-bearing 1522 is H5. The outer diameter of the shaft shoulder of the second sub-bearing 1522 is D11.

[0110] In some embodiments, referring to FIG. 11, the height of the first shaft section 111 is H6. When H5 / H6×D5 / D11>0.2, in this range, the first bearing 152 has small radial deformation and small stress, which is beneficial to reduce wear and improve reliability. FIG. 26 shows a relationship diagram of H5 / H6×D5 / D11 and the radial deformation of the first bearing 152.

[0111] In some embodiments, referring to FIG. 4, the height of the middle partition plate 160 is H7, and the height of the first cylinder 122 is H2, which is the same as the height of the second cylinder 121. When H7 / H2∈[0.22, 0.35], in this range, the compressor has high energy conversion efficiency (COP). FIG. 27 shows a relationship diagram of H7 / H2 and the COP efficiency of the compressor.

[0112] [Structure of bearing and compressor body shell]

[0113] In some embodiments, the first bearing 152 of the compression mechanism 14 is fixed to the inner circumferential wall of the first shell 11 of the compressor body 1 by welding to achieve the installation of the compression mechanism 14 in the inner cavity of the first shell 11. For example, in a double-cylinder compressor, the first bearing 152 is welded to the inner wall of the first shell 11.

[0114] The number of welding points between the bearing and the inner wall of the shell affects the welding strength, welding deformation, and welding efficiency. If the number of welding points is small, the welding strength is not enough, which can easily cause the compression mechanism 14 to fall off and cause danger. If the number of welding points is large, the bearing or the cylinder is prone to deformation, which can reduce the air tightness and affect the welding efficiency.

[0115] To solve the above technical problems, in some embodiments of the present disclosure, the weight of the compression mechanism 14, the number of bearing welding points, and other parameters are optimized to improve the installation reliability of the compression mechanism 14 and meet the high-speed requirement of the compressor.

[0116] For example, referring to FIG. 16, the inner diameter of the first shell 11 of the compressor is D14, the number of welding points between the first bearing 152 and the first shell 11 is N, and the weight of the compression mechanism 14 is G. G / N ∈ [1, 4], and D14 / N ∈ [25, 45]. Within this range, the high-speed requirement of the compressor, the 500 times gravity requirement, and the air leakage requirement can be considered and met.

[0117] In some embodiments, the motor 13 and the compression mechanism 14 need to be matched in the height direction. When the welding height of the compression mechanism 14 is low, the lower the position of the compression mechanism 14 and the motor 13 in the first shell 11, the lower the height of the center of mass of the compressor, which is positively correlated with the welding height of the compression mechanism 14. This is beneficial to improve the stability of the compressor.

[0118] In some embodiments, the welding height of the compression mechanism 14 determines the size of the oil pool of the compressor. Generally, after the compressor is filled with oil, the oil surface does not exceed the upper surface of the first cylinder 122. The filling amount of the refrigeration oil is determined by the refrigerant filling amount of the air conditioning system, and the refrigerant filling amount is related to the displacement of the compressor. Therefore, after the displacement of the compressor is determined, the filling amount of the refrigeration oil is basically determined, thereby determining the size of the oil pool.

[0119] Referring to FIG. 1A, the distance between the welding point position of the first bearing 152 and the bottom of the first shell 11 is H15, the height of the first shell 11 is H16, and H15 / H16 ∈ [0.35, 0.45]. This range meets the volume requirement of the oil pool of the compressor and makes the center of mass of the compressor low.

[0120] [Structure of eccentric crankshaft]

[0121] In some embodiments, the inner cavity of the first shell 11 of the compressor body 1 forms an oil pool.

[0122] The eccentric crankshaft 110 is provided with an oil supply channel 116 extending along the axial direction of the eccentric crankshaft 110. The oil supply channel 116 is configured to supply oil in the oil pool to friction pairs on the eccentric crankshaft 110, such as bearings, cylinders, pistons, etc.

[0123] Referring to FIG. 11, the oil supply channel 116 penetrates the eccentric crankshaft 110. The top of the oil supply channel 116 is provided with a shaft plug 118. The inner hole diameter of the shaft plug 118 is D1, and the diameter of the oil suction port 1191 at the bottom of the oil supply channel 116 is D2. The time from the initial start of the compressor to the stable oil supply of each friction pair is the oiling time, which will be longer as the D1 / D2 ratio decreases. The longer the time, the longer the time of dry friction and mixed friction of each friction pair such as bearings, which will easily cause wear of each friction pair of the compressor during the start-up stage.

[0124] In addition, when the compressor is running at high speed under heavy load, lubricating oil droplets will enter the air conditioning refrigeration system with high-pressure refrigerant, which will reduce the lubricating oil in the compressor and increase the risk of dry friction between parts, reducing the operation reliability of the compressor. If the oil discharge rate is high, the air conditioner needs to return oil frequently, and because the air conditioning refrigeration system is designed as an internal spiral, the lubricating oil adhering to the copper pipe will also reduce the heat exchange capacity of the heat exchanger.

[0125] To solve the above technical problems, in some embodiments of the present disclosure, the oil supply channel 116 of the eccentric crankshaft 110 and the shaft plug 118 are optimized to shorten the oiling time during the initial start of the compressor, reduce the wear of each friction pair, and reduce the oil discharge rate.

[0126] For example, referring to FIG. 11, the oil supply channel 116 includes a first oil supply channel 1161 and a second oil supply channel 1162 in communication, the inner diameter of the first oil supply channel 1161 is D3, the inner diameter of the second oil supply channel 1162 is D4, and the diameter of the oil suction port at the bottom of the second oil supply channel 1162 is D2.

[0127] In some embodiments, referring to FIG. 4, the second oil supply channel 1162 is provided with an oiling vane 117 to provide oil conveying power. When the compressor is running, the motor 13 drives the eccentric crankshaft 110 to rotate, at which time the oiling vane 117 rotates synchronously with the eccentric crankshaft 110, a negative pressure is formed at the bottom oil suction port of the eccentric crankshaft 110, and the lubricating oil in the oil pool enters the oil supply channel 116 through the oil suction port and then flows to each friction pair.

[0128] The shaft plug 118 is arranged in the first oil supply channel 1161, and the shaft plug 118 is arranged close to the top of the first oil supply channel 1161. The inner hole diameter of the shaft plug 118 is D1.

[0129] The initial start-up of the compressor to each friction pair is stably supplied with oil. The oil supply time is longer as the D1 / D2 ratio decreases. The D1 / D2 ratio is set to be in the range of [0.13, 0.65], so that the initial oil supply time is short.

[0130] FIG. 21 shows the relationship between the initial oil supply time of the compressor and the D1 / D2 ratio. Referring to FIG. 21, when the D1 / D2 ratio increases from 0.13 to 0.65, the initial oil supply time decreases from 1 s to about 0.56 s.

[0131] The oil discharge rate of the compressor is related to the value of (D2+D1) / (D4-D3). The greater the value of (D2+D1) / (D4-D3), the higher the oil discharge rate. The value of (D2+D1) / (D4-D3) is set to be in the range of [0.3, 1.19], so that the oil discharge rate is reduced.

[0132] FIG. 22 shows the relationship between the oil discharge rate and the value of (D2+D1) / (D4-D3). Referring to FIG. 22, when the value of (D2+D1) / (D4-D3) decreases from 1.19 to 0.3, the oil discharge rate decreases from about 2.1 to about 0.7.

[0133] In some embodiments, referring to FIG. 11, the bottom of the second oil supply channel 1162 is provided with an oil suction pipe 119, and the oil suction pipe 119 is inserted into the second oil supply channel 1162. The oil suction pipe 119 is inserted into the bottom of the second oil supply channel 1162 in an interference fit, so as to be fixedly installed on the eccentric crankshaft 110. The bottom of the oil suction pipe 119 is provided with an oil suction port 1191, and the diameter of the oil suction port is D2. The diameter of the oil suction port 1191 is smaller than the inner diameter of the oil suction pipe 119. That is, the bottom of the oil suction pipe 119 is a reduced port structure.

[0134] In some embodiments, if the diameter of the oil suction port 1191 is large, the amount of oil entering the oil supply channel 116 can be increased, but the pumping head is low, which leads to a low oil rising height. If the diameter of the oil suction port 1191 is small, the amount of oil entering the oil supply channel 116 is reduced, but the pumping head is high, which is beneficial to oil supply at low speed.

[0135] In some embodiments of the present disclosure, the ratio between the diameter D2 of the oil suction port 1191 and the inner diameter D4 of the second oil supply channel 1162 is in the range of [0.3, 1]. In this range, the oil supply effect of the compressor is improved.

[0136] In some embodiments, when the compressor operates at a low frequency, the eccentric crankshaft 110 has a small oil suction amount, and only a small amount of oil in the oil pool is transferred to the upper space of the motor 13 inside the compressor and the outside of the compressor, so that the oil level in the oil pool can be maintained at a high level. When the compressor operates at a high frequency, the eccentric crankshaft 110 has a large oil suction amount, and a large amount of oil is transferred to the upper space of the motor 13 and the outside of the compressor, and the oil level in the oil pool is thus greatly reduced. Therefore, when the compressor operates at a high speed, increasing the insertion depth of the oil suction port of the eccentric crankshaft 110 into the oil pool is an important measure to maintain the oil level.

[0137] In a double-cylinder compressor, referring to FIG. 4, the height of the first cylinder 122 is H2, the height distance between the central axis of the intake port of the first cylinder 122 and the oil suction port is H1, and H1 / H2=h. The rated limit operating frequency of the compressor is t, and t / h∈[20, 80]. This range can ensure the oil supply amount of the eccentric crankshaft 110 and meet the oil supply demand of the friction pair.

[0138] In a single-cylinder compressor, the height of the cylinder is H2, the height distance between the central axis of the intake port of the cylinder and the oil suction port is H1, H1 / H2=h, and the rated limit operating frequency of the compressor is t, t / h∈[20, 80]. This range can ensure the oil supply amount of the eccentric crankshaft 110 and meet the oil supply demand of the friction pair.

[0139] [Exhaust structure of eccentric crankshaft]

[0140] When the compressor is stationary, the oil level inside the eccentric crankshaft 110 is the same as the outside, and at this time, a part of the upper part of the eccentric crankshaft 110 is filled with refrigerant gas. After the compressor starts to operate, the gas in this part is first exhausted from the eccentric crankshaft 110, and then the oil in the bottom oil pool is sucked in. Therefore, an exhaust hole needs to be opened on the eccentric crankshaft 110 for exhaust. However, when the compressor speed gradually increases, the oil level inside the eccentric crankshaft 110 will rise, and at this time, the oil will fill the internal space, and at the same time, a part of the oil will be exhausted from the exhaust hole. This part of the oil will flow to the upper part of the motor 13 along with the refrigerant gas, and finally may flow out of the compressor, increasing the oil discharge rate of the compressor and affecting the reliability. Therefore, the ideal function of the exhaust hole is to only exhaust gas and not oil. Usually, the compressor reduces the hole diameter of the exhaust hole to minimize the discharge of oil, but cannot completely avoid it, and the effect is not good.

[0141] To solve the above technical problems, in some embodiments of the present disclosure, the exhaust hole on the eccentric crankshaft 110 is structurally improved to effectively avoid the discharge of oil from the exhaust hole when the compressor operates at a high speed, and to reduce the oil discharge rate.

[0142] For example, referring to FIG. 12A and FIG. 12B, the eccentric crankshaft 110 is provided with an exhaust passage 410, which is in communication with the oil supply passage 116, and is configured to exhaust the gas in the oil supply passage 116.

[0143] In some embodiments, the first shaft section 111 is provided with an exhaust passage 410, which is in communication with the first oil supply passage 1161.

[0144] The exhaust passage 410 is provided with a passage member 420. The passage member 420 is formed with a through auxiliary passage 423. The auxiliary passage 423 is in communication with the exhaust passage 410, and the inner diameter of the auxiliary passage 423 has a decreasing trend along the exhaust direction of the gas in the exhaust passage 410.

[0145] For example, the passage member 420 is a metal structure member, which is interference-fitted into the exhaust passage 410 to achieve fixed installation of the passage member 420 in the exhaust passage 410.

[0146] The auxiliary passage 423 is provided with a moving member 430. The moving member 430 is configured to move along the auxiliary passage 423 to open or close the auxiliary passage 423.

[0147] The moving member 430 is a metal ball located in the auxiliary passage 423. The metal ball moves along the auxiliary passage 423. When the metal ball moves to a first position, the metal ball closes the auxiliary passage 423, and at this time, the oil cannot be exhausted through the exhaust passage 410 and the auxiliary passage 423. When the metal ball moves to a second position, the metal ball opens the auxiliary passage 423, and at this time, the refrigerant gas is exhausted through the exhaust passage 410 and the auxiliary passage 423.

[0148] Through the movement of the moving member 430 in the auxiliary passage 423, the closing or opening of the auxiliary passage 423 is achieved, and since the auxiliary passage 423 is in communication with the exhaust passage 410, the closing or opening of the exhaust passage 410 is also achieved. In combination with the operating frequency of the compressor, the effect of exhausting oil at low frequency and not exhausting oil at high frequency of the compressor is achieved.

[0149] In some embodiments, referring to FIG. 13 and FIG. 14, the inner diameter of the auxiliary passage 423 has a decreasing trend in the direction from the first end 421 to the second end 422, the outer diameter of the moving member 430 is greater than the lower limit value of the inner diameter of the auxiliary passage 423, and the outer diameter of the moving member 430 is less than the upper limit value of the inner diameter of the auxiliary passage 423.

[0150] The auxiliary passage 423 is a conical passage structure, and the moving member 430 is a spherical structure. The outer diameter of the moving member 430 is less than the inner diameter of the first end 421 of the auxiliary passage 423 and greater than the inner diameter of the second end 422.

[0151] For example, when the moving piece 430 moves towards the second end 422 close to the auxiliary passage 423, the outer peripheral wall of the moving piece 430 abuts against the inner peripheral wall of the auxiliary passage 423, thereby plugging the auxiliary passage 423, and thus the oil can be prevented from being discharged through the exhaust passage 410 when the compressor is operated at a high frequency.

[0152] For another example, when the moving piece 430 moves towards the first end 421 close to the auxiliary passage 423, a gap is formed between the outer peripheral wall of the moving piece 430 and the inner peripheral wall of the auxiliary passage 423, thereby opening the auxiliary passage 423, and thus the refrigerant gas can be discharged through the exhaust passage 410.

[0153] In some embodiments, referring to FIGS. 13 and 14, the passage piece 420 is provided with a plurality of stop portions 424, which are arranged at intervals along the circumference of the auxiliary passage 423, and are configured to limit the moving piece 430 within the auxiliary passage 423.

[0154] In some embodiments, the stop portion 424 is a plurality of rib structures, and is an integral structure with the passage piece 420 and is integrally formed on the first end 421 of the passage piece 420. When the moving piece 430 moves to the first end 421 of the passage piece 420, the stop portion 424 limits the moving piece 430, thereby preventing the moving piece 430 from being pulled out of the auxiliary passage 423.

[0155] When the moving piece 430 is installed into the auxiliary passage 423, the moving piece 430 is inserted into the auxiliary passage 423 from the first end 421 of the passage piece 420. Since the stop portion 424 is a rib structure, the rib structure deforms under stress to allow the moving piece 430 to be inserted into the auxiliary passage 423 through the first end 421 with a large diameter. After the moving piece 430 is inserted, the rib structure returns to its original shape to limit the moving piece 430.

[0156] In some embodiments, the plurality of stop portions 424 are arranged on the first end 421 of the passage piece 420, and the stop portion 424 includes an integral structure of an extension section 4241 and an extension section 4242, which are arranged at an angle, for example, at an angle of 90 degrees. The extension section 4241 extends away from the passage piece 420 from the first end 421, and the extension section 4242 extends axially towards the auxiliary passage 423 from the extension section 4241.

[0157] The extension section 4242 constitutes a limiting claw to limit the moving piece 430, thereby preventing the moving piece 430 from being pulled out of the first end 421 of the passage piece 420.

[0158] In some embodiments, referring to FIG. 12A, the exhaust passage 410 extends obliquely upward from the oil supply passage 116.

[0159] When the operating frequency of the compressor is less than the set frequency, the moving member 430 is close to the first end 421 of the passage member 420 to open the auxiliary passage 423.

[0160] In some embodiments, when the operating frequency of the compressor is less than the set frequency, the centrifugal force of the moving member 430 in the oblique direction f' is less than the gravitational force in the oblique direction g', at this time, the moving member 430 is still at the bottom, that is, the moving member 430 is located at the first end 421 of the passage member 420, and since the outer diameter of the moving member 430 is less than the inner diameter of the first end 421 of the passage member 420, there is a gap between the moving member 430 and the auxiliary passage 423, and the refrigerant gas flows out of the eccentric crankshaft 110 through the auxiliary passage 423.

[0161] When the operating frequency of the compressor is greater than the set frequency, the moving member 430 is close to the second end 422 of the passage member 420 to close the auxiliary passage 423.

[0162] In some embodiments, when the operating frequency of the compressor is greater than the set frequency, the centrifugal force of the moving member 430 in the oblique direction f' is greater than the gravitational force in the oblique direction g', at this time, the moving member 430 moves upward, that is, moves toward the second end 422 of the passage member 420, and the moving member 430 blocks the auxiliary passage 423, at this time, the oil cannot be discharged from the auxiliary passage 423.

[0163] The inclination angle of the auxiliary passage 423 needs to be designed in association with the gravitational force of the moving member 430 and the frequency h at which the compressor stops discharging and starts discharging oil.

[0164] In some embodiments, referring to FIGS. 12A, 13 and 14, the discharge passage 410 extends horizontally from the oil supply passage 116, and correspondingly, the auxiliary passage 423 also extends horizontally, and the spring 440 is arranged in the auxiliary passage 423.

[0165] When the operating frequency of the compressor is less than the set frequency, the centrifugal force of the moving member 430 is less than the elastic force of the spring 440, the spring 440 pushes the moving member 430 close to the first end 421 of the passage member 420, and there is a gap between the moving member 430 and the auxiliary passage 423, and the refrigerant gas flows out of the eccentric crankshaft 110 through the auxiliary passage 423.

[0166] When the operating frequency of the compressor is greater than the set frequency, the centrifugal force of the moving member 430 is greater than the elastic force of the spring 440, the moving member 430 moves close to the second end 422 of the passage member 420, and the spring 440 is compressed by the moving member 430, and since the outer diameter of the moving member 430 is greater than the inner diameter of the second end 422 of the auxiliary passage 423, the moving member 430 closes the auxiliary passage 423, and the oil cannot be discharged from the auxiliary passage 423.

[0167] The spring 440 needs to be designed in association with the end of exhaust and the frequency h of the start of oil discharge.

[0168] In some embodiments, the exhaust passage 410 exhausts gas into the space between the motor 13 and the bearing. Taking a double-cylinder compressor as an example, the exhaust passage 410 exhausts gas into the space between the motor 13 and the first bearing 152.

[0169] In some embodiments, the exhaust passage 410 has an auxiliary passage 423 therein, the auxiliary passage 423 is in communication with the exhaust passage 410, and the inner diameter of the auxiliary passage 423 has a decreasing trend along the exhaust direction of the gas in the exhaust passage 410.

[0170] The auxiliary passage 423 is provided with a moving member 430. The moving member 430 is configured to move along the auxiliary passage 423 to open or close the auxiliary passage 423.

[0171] When the operating frequency of the compressor is greater than the set frequency, the moving member 430 closes the auxiliary passage 423, and low-frequency exhaust is achieved.

[0172] When the operating frequency of the compressor is less than the set frequency, the moving member 430 opens the auxiliary passage 423, and high-frequency oil discharge is avoided.

[0173] The auxiliary passage 423 is formed by a passage member 420, that is, the passage member 420 is assembled into the exhaust passage 410 by interference, the passage member 420 is formed with a through auxiliary passage 423 therein, and the auxiliary passage 423 is in communication with the exhaust passage 410.

[0174] In some embodiments, the inner diameter of the first shell of the compressor is greatly affected by the displacement, and generally, the larger the displacement, the larger the inner diameter of the first shell; and when the displacement is larger, in order to reduce the oil discharge rate and the pressure loss of the refrigerant gas, the inner diameter of the exhaust pipe also needs to be larger.

[0175] Therefore, the inner diameter of the first shell 11 is set as D14, referring to FIGS. 1A, 3 and 5, the exhaust pipe 12 is arranged at the top of the first shell 11, the inner diameter of the exhaust pipe 12 is D16, and D1 / D16∈[8, 12], which can reduce the oil discharge rate and the pressure loss of the refrigerant gas of the compressor.

[0176] [Structure of motor]

[0177] In some embodiments, the inner diameter of the first shell 11 determines the limit size of the motor 13. If the outer diameter of the rotor 320 is too large, the amount of the stator 310 core will be reduced, the magnetic density of the stator 310 core is high, the iron loss of the motor 13 is high, which is not conducive to the efficiency of the motor 13; at the same time, the rotor 320 is a moving body, if the volume is large, it will have an adverse effect on the noise. If the outer diameter of the rotor 320 is small, the amount of the magnet is small, the magnetic flux of the permanent magnet is low, the noise is low, but it will have an adverse effect on the efficiency and high power of the motor 13. In addition, the thickness of the motor 13 stator and rotor is the vertical dimension, which acts together with the inner diameter of the first shell 11 and the outer diameter of the rotor 320, and affects the volume of the motor 13, which has an effect on the noise and performance of the motor 13.

[0178] Based on this, in some embodiments of the present disclosure, the inner diameter of the shell, the height of the stator and rotor, and the outer diameter of the rotor 320 are optimized to improve the efficiency of the motor 13 and reduce the noise.

[0179] In some embodiments, referring to FIG. 16, the inner diameter of the first shell 11 is D14, referring to FIGS. 6 and 7, the height of the rotor 320 is H8, and the outer diameter of the rotor 320 is D9, D14 / (H8xD9) ∈ (0.028, 0.032), which is conducive to reducing the noise of the compressor while improving the efficiency of the motor 13. FIG. 34 is a graph of the relationship between D14 / (H8xD9) and the noise of the compressor and the efficiency of the motor.

[0180] In some embodiments, the gap between the stator 310 and the rotor 320 of the motor 13 and the thickness of the stator and rotor have a relationship with the size of the magnetic flux density of the motor 13. The larger the magnetic flux density of the motor 13, the greater the magnetostriction of the motor 13, which leads to a large electromagnetic noise of the motor 13. The smaller the magnetic flux density, the lower the efficiency of the motor 13.

[0181] The gap between the stator 310 and the rotor 320 of the motor 13 and the thickness of the stator and rotor have a proportional relationship with the total height of the first shell 11 of the compressor, which affects the oiling and oil return of the compressor. If the height of the motor 13 accounts for a small proportion of the total height of the first shell 11, the proportion of the upper and lower cavities of the motor 13 is large, and the oil guiding of the motor section is relatively easy. If the gap between the stator 310 and the rotor 320 is small, and the thickness of the stator and rotor 320 is high, the motor section is long and difficult to guide oil, which can cause excessive oil storage in the upper cavity of the motor 13.

[0182] Based on this, in some embodiments, referring to FIG. 1A, the height of the first shell 11 is H16, referring to FIG. 7, the height of the rotor 320 is H8, the gap between the stator 310 and the rotor 320 is S, and H16 / (H8xS) ∈ (6.5, 9.5), which is conducive to limiting and balancing the noise of the compressor, improving the efficiency, and improving the problem of oil storage in the upper cavity of the motor 13. FIG. 35 is a graph of the relationship between H16 / (H8xS) and the noise and efficiency of the motor.

[0183] In some embodiments, the smaller the silicon steel sheet thickness of the motor 13, the lower the iron loss, the higher the efficiency, and the greater the centrifugal force at high speed, and the silicon steel sheet of the rotor 320 is prone to breakage.

[0184] Therefore, the silicon steel sheet thickness of the rotor 320 / the silicon steel sheet thickness of the stator 310 is set to any value in [1.15, 1.75] to ensure the efficiency of the motor 13 while improving the anti-breakage capability of the rotor 320.

[0185] In some embodiments, in the rotor 320 compressor, the efficiency of the permanent magnet synchronous motor is inversely proportional to the motor loss, and the lower the motor loss, the higher the motor efficiency. The motor loss is mainly composed of copper loss of copper wire and iron loss of silicon steel. Under the premise of keeping the motor cost basically unchanged, the change of the motor shape will cause the change of the copper loss and the iron loss of the motor. For example, increasing the stator slot area will increase the amount of copper and reduce the weight of the silicon steel, and the copper loss and the iron loss of the motor will change.

[0186] Therefore, the weight of the stator 310 is set to G1, the weight of the rotor 320 is set to G2, and G1 / G2∈(3.2, 5.2). Within this range, it is beneficial to reduce the copper loss and the iron loss of the motor 13 and improve the efficiency of the motor 13.

[0187] In some embodiments, when the compressor adopts a high-speed motor (such as a motor with a maximum speed of 140 rps or more), the back electromotive force at low speed (such as a speed of 5-15 rps) is low, which causes the compressor to run unstably or unable to run. In order to meet the design requirements of high speed, the height of the motor is increased, which in turn increases the length of the eccentric crankshaft 110, which aggravates the deformation of the eccentric crankshaft 110 and easily causes the sweep bore.

[0188] To solve the above technical problems, in some embodiments of the present disclosure, the diameter of the copper wire of the motor 13 is set to d1, the thickness of the silicon steel sheet of the motor 13 is set to d2, and d1 / d2∈(1.5, 8].

[0189] It should be noted that the gap between the stator 310 and the rotor 320 is set to S, the height of the motor 13 is set to d4, and d4 / S∈(50, 150].

[0190] The above interval setting can meet the design requirements of high speed and low speed of the compressor, and at the same time ensure the efficiency of the compressor. FIG. 36 shows the relationship between d1 / d2 and the motor efficiency and speed. FIG. 37 shows the relationship between d4 / S and the motor efficiency and the deformation amount of the eccentric crankshaft 110.

[0191] In some embodiments, referring to FIG. 3, the top of the first shell 11 is provided with an exhaust pipe 12.

[0192] Referring to FIG. 1A, the compressor body 1 further comprises an oil equalization pipe 15, one end of the oil equalization pipe 15 is connected with the first shell 11 and communicates with the inner cavity of the first shell 11, the other end of the oil equalization pipe 15 is connected with the exhaust pipe 12, and the connection position of the oil equalization pipe 15 with the first shell 11 is lower than the first bearing 152.

[0193] The distance between the connection position of the oil equalization pipe 15 with the first shell 11 and the bottom of the first shell 11 is H17. The distance between the axis of the suction port of the first cylinder 122 and the bottom of the first shell 11 is H18, and H17 / H18 ∈ [0.9, 1.2]. This range helps to improve the COP efficiency of the compressor.

[0194] In some embodiments, referring to FIG. 15, the height of the stator 310 is H19, the outer diameter of the stator 310 is D15, a plurality of spaced convex portions 311 and concave portions 312 are arranged on the outer circumferential wall of the stator 310, the convex portions 311 are fixedly connected with the inner wall of the first shell 11, the area of the plurality of convex portions 311 is S1, and S1 / π×D15×H19 ∈ [0.35, 0.5]. This range takes into account the efficiency of the motor 13 and Optical Character Recognition (OCR).

[0195] In some embodiments, referring to FIG. 1A and FIG. 3, the inner diameter of the first shell 11 is D14, the exhaust pipe 12 is arranged at the top of the first shell 11, the inner diameter of the exhaust pipe 12 is D16, the distance height between the bottom end of the exhaust pipe 12 and the top end of the eccentric crankshaft 110 is H20, and D14 / (D16×H20) ∈ (3.81, 4.62). This range is beneficial to reduce the oil discharge rate of the compressor.

[0196] [Compressor body] The amplitude value of the compressor has a large contribution to the noise of the outdoor unit. Generally, the vibration noise of the compressor is reduced by arranging a damping device (foot) at the bottom of the compressor, which belongs to passive damping, and sometimes the effect is not good.

[0197] To solve the above technical problems, in some embodiments of the present disclosure, the vibration of the compressor is effectively suppressed by actively damping the compressor, thereby reducing the vibration noise of the compressor and the air conditioner.

[0198] For example, referring to FIG. 2A and FIG. 2B, a sensor 510 (acceleration sensor) is arranged on the circumferential wall of the first shell 11, and the sensor 510 is configured to obtain a tangential vibration first signal (such as a time domain signal) of the first shell 11.

[0199] The circumferential wall of the first shell 11 is provided with an exciter 520 (inertial exciter) configured to emit a second signal (such as an excitation signal) of equal amplitude and opposite phase according to the tangential vibration first signal acquired by the sensor 510, so as to reduce the vibration of the compressor.

[0200] The sensor 510 and the exciter 520 are fixedly installed outside the circumferential wall of the first shell 11, are convenient to disassemble, do not occupy the internal space of the first shell 11, and do not interfere with the installation of the internal motor 13 and the compression mechanism 14.

[0201] The exciter 520 generates a second signal of equal amplitude and opposite phase with the first shell 11 to actively reduce the vibration of the compressor, effectively suppressing the vibration of the compressor.

[0202] In some embodiments, the compressor comprises a processor 530 (data processor) configured to receive the tangential vibration first signal acquired by the sensor 510 and transmit the first signal to the exciter 520 after reversing the phase of the first signal by 180°.

[0203] The air conditioner further comprises a controller comprising the processor 530. The processor 530 can include a central processing unit (CPU), a microprocessor, an application specific integrated circuit (ASIC), and can be configured to perform the corresponding operations described in the controller when the processor 530 executes a program stored in a non-transitory computer readable medium coupled to the controller.

[0204] It should be noted that the controller is coupled to the sensor 510 and the exciter 520, respectively.

[0205] When the compressor is working, the sensor 510 acquires the tangential vibration first signal of the first shell 11 and transmits it to the data processor 530. By using the time-frequency analysis method, the phase of the first signal is reversed by 180°, and then the first signal is transmitted to the exciter 520. The exciter 520 emits a second signal of equal amplitude and opposite phase with the compressor, so that the vibration of the compressor is effectively suppressed, and active vibration reduction and noise reduction are achieved.

[0206] [Structure of gas-liquid separator]

[0207] The gas-liquid separator 2 is one of the important sources of noise generation and radiation while protecting the compressor body 1. On the one hand, the compressor body 1 is a vertical rotor type, and if there is no gas-liquid separator, the rotation center should be the geometric center position of the compressor body 1; but if there is a gas-liquid separator 2, the center of mass of the compressor body 1 deviates from the rotation center, thereby causing the compression vibration to increase. Since the rotation center of the gas-liquid separator 2 is the farthest, the vibration acceleration of the edge of the gas-liquid separator 2 is also the largest. On the other hand, from the formula I = mr2 of the moment of inertia, when the mass of the object cannot be increased, the moment of inertia of the compressor body 1 can be increased by increasing the radius of gyration r, and the larger the moment of inertia, the more stable the object rotates.

[0208] Therefore, there is a certain proportional relationship between the distance between the rotation center of the gas-liquid separator 2 and the rotation center of the compressor body 1, and by properly optimizing the proportional relationship, the effect of reducing the vibration and noise of the compressor can be achieved.

[0209] Based on this, in some embodiments of the disclosure, the diameter and height between the gas-liquid separator 2 and the compressor body 1 are optimized to reduce the vibration and noise of the compressor.

[0210] For example, referring to FIG. 1A, the outer diameter of the first shell 11 of the compressor body 1 is D12, and the height of the compressor body 1 is H12. The outer diameter of the second shell 21 of the gas-liquid separator 2 is D13, and the height of the gas-liquid separator 2 is H13.

[0211] It should be noted that D13 / D12 ∈ (0.45, 0.56), H13 / H12 ∈ (0.4, 0.6), and this range helps to reduce the vibration of the gas-liquid separator 2.

[0212] In some embodiments, referring to FIG. 16, the compressor further includes a bracket 200 configured to connect the first shell 11 and the second shell 21. The bracket 200 is welded with the first shell 11, the number of welding points between the bracket 200 and the first shell 11 is n, the inner diameter of the first shell 11 is D14, and the height of the first shell 11 is H16, D14 / n × 10 ∈ (6, 7.5), and H16 / n × 20 ∈ (4.5, 6).

[0213] The above setting can effectively increase the frequency of the rigid body torsional mode of the gas-liquid separator 2 without increasing the process flow and welding cost, thereby reducing the probability of abnormal noise generation of the compressor.

[0214] In some embodiments, referring to FIGS. 16-18, the compressor includes two symmetrically arranged brackets 200 configured to connect the first shell 11 and the second shell 21.

[0215] The bracket 200 comprises a bracket first part 210, a bracket second part 220, a bracket third part 230 and a bracket fourth part 240 connected in sequence. The bracket first part 210 and the bracket third part 230 are located on the same side of the bracket second part 220, the bracket second part 220 and the bracket fourth part 240 are located on different sides of the bracket third part 230, the bracket second part 220 is adapted to the outer contour of the second shell 21 and is fixedly connected, such as welded. The bracket first part 210 and the bracket third part 230 extend between the first shell 11 and the second shell 21 respectively. The bracket first part 210 and the bracket fourth part 240 are fixedly connected with the first shell 11, such as welded. The length of the bracket first part 210 is greater than the length of the bracket third part 230, and the two bracket fourth parts 240 are close to each other.

[0216] It should be noted that the length of the bracket first part 210 is the distance from the end of the bracket first part 210 close to the gas-liquid separator 2 to the end of the bracket first part 210 close to the compressor body 1. In addition, the length of the bracket third part 230 is the distance from the end of the bracket third part 230 close to the gas-liquid separator 2 to the end of the bracket third part 230 close to the compressor body 1.

[0217] For each bracket 200, two places of the first shell 11 are fixed by welding the bracket first part 210, the bracket fourth part 240 and the first shell 11. When the two brackets 200 are used together, there are four places of the first shell 11 fixed, which improves the connection stability of the bracket 200 and the first shell 11.

[0218] When the two brackets 200 are used together, the two bracket second parts 220 jointly clamp the gas-liquid separator 2, which improves the connection stability of the bracket 200 and the second shell 21.

[0219] In some embodiments, an opening 250 is arranged on the bracket first part 210, the opening 250 extends along the length direction of the bracket first part 210, the width of the opening 250 is H14, the length of the opening 250 is L1, and H14 / L1∈(0, 0.82].

[0220] By changing the size of the opening 250, the connection stiffness of the gas-liquid separator 2 can be changed, which is conducive to optimizing the natural frequency and obtaining the required natural frequency.

[0221] In some embodiments, the width of the bracket second part 220 is W3, the outer contour radius of the second shell 21 is R2, and the range of W3 / R2 is [1.4, 2.2]. Within this range, it is helpful to improve the natural frequency of the gas-liquid separator 2.

[0222] In some embodiments, the distance from the intersection of the first bracket part 210 and the second bracket part 220 to the symmetry plane of the two brackets 200 is W1, the distance from the third bracket part 230 to the symmetry plane of the two brackets 200 is W2, the outer contour radius of the second shell 21 is R2, the outer contour radius of the first shell 11 is R1, and (W1 / R2)×(W2 / R1)>0.3. Within the above range, the double torsional frequency of the gas-liquid separator 2 tends to be stable, the solid top frequency is raised to above 510 Hz, and the gas-liquid separator 2 is suitable for a double-cylinder compressor with a maximum rotational speed of 180 rps.

[0223] In some embodiments, (W1 / R2)×(W2 / R1)<1, which is conducive to reducing the vibration of the compressor body 1 and the gas-liquid separator 2.

[0224] In some embodiments, the first bracket part 210 includes a one-piece first bracket part one section 211 and a first bracket part two section 212. The first bracket part one section 211 extends outwardly and obliquely from the first end of the first bracket part two section 212. The first bracket part one section 211 is adapted to and fixedly connected to the first shell 11. The second end of the first bracket part two section 212 is connected to the second bracket part 220.

[0225] In some embodiments, referring to FIGS. 19 and 20, the bracket 200 includes a bracket body part 260. Bracket extension parts 270 are symmetrically arranged at opposite ends of the bracket body part 260. For example, the plane formed by the axis of the compressor body 1 and the axis of the gas-liquid separator 2 is a first reference plane. The bracket extension parts 270 are symmetric about the first reference plane.

[0226] The bracket body part 260 is adapted to and fixedly connected to the outer contour of the first shell 11, such as by welding.

[0227] In some embodiments, the bracket extension part 270 includes a one-piece extension part one section 271 and an extension part two section 272. The extension part one section 271 is connected between the bracket body part 260 and the extension part two section 272. The extension part two section 272 is fixedly connected to the outer contour of the second shell 21, such as by welding.

[0228] For example, the outer contour radius of the first shell 11 is R1, the outer contour radius of the second shell 21 is R2, and the distance between the extension part one section 271 and the symmetry plane of the bracket 200 is W4. 2W4 / (R1+R2)∈[0.35, 0.55]. Within this range, it is conducive to reducing the vibration of the gas-liquid separator 2.

[0229] In some embodiments, the distance between the welding point 280 between the support body part 260 and the first shell 11 and the symmetry plane of the support 200 is W5, and W5 / W4>0.75. As W5 / W4increases, the vibration of the gas-liquid separator 2 tends to decrease, and when it is greater than 0.75, the vibration of the gas-liquid separator 2 does not obviously improve.

[0230] In some embodiments, if 1>W5 / W4, for example, W5 / W4is 0.8 or 0.9, the vibration of the gas-liquid separator 2 is small.

[0231] [Compressor vibration reduction device]

[0232] In order to reduce the vibration of the compressor, a vibration reduction device 415 (such as a vibration isolation foot pad) can be used to reduce the vibration of the compressor.

[0233] For example, the vibration reduction device 415 can be adjusted from the perspective of stiffness matching and damping matching, so that the vibration of the compressor can be reduced. However, as the volume and weight of the compressor increase, the stiffness of the vibration reduction device 415 will decrease. If the stiffness of the vibration reduction device 415 is lower than a predetermined threshold, the compressor is prone to excessive shaking during transportation, which can impact the pipeline and cause pipeline rupture and other problems.

[0234] In order to solve the above technical problems, in some embodiments of the present disclosure, referring to FIG. 1B, the compressor further comprises a mounting part 416 connected with the first shell 11. The compressor further comprises a mounting hole 417. Through the matching of the connecting piece (such as a bolt) and the mounting hole 417, the connection between the vibration reduction device 415 and the mounting part 416 can be achieved, and the vibration reduction device 415 is configured to bear the compressor body of the compressor. By optimizing the vibration reduction device 415 of the compressor, the vibration reduction effect can be improved.

[0235] In some embodiments, referring to FIGS. 1A and 1B, the height of the first shell 11 is H16, and the height of the vibration reduction device 415 is H21.

[0236] In some embodiments, since the height of the first shell 11 is fixed, if 4.5>H16 / H21, the height of the vibration reduction device 415 will be too high, which will increase the cost of manufacturing the vibration reduction device 415, and in addition, it will also affect the stability of the operation of the compressor and increase the risk of the compressor tipping over.

[0237] In some embodiments, since the height of the first shell 11 is fixed, if 4.5

[0238] In some embodiments, due to the fixed height of the first shell 11, if 6.5≤H16 / H21, the height of the damping device 415 is too low, which results in poor damping effect of the damping device 415 on the compressor vibration, and the lower shell of the compressor may also rub against the ground when the compressor vibrates.

[0239] In some embodiments, due to the fixed height of the first shell 11, if 6.5>H16 / H21, as H16 / H21 decreases, the height of the damping device 415 increases, which is beneficial to reduce the vibration of the compressor, reduce the noise generated by the compressor vibration, and avoid the lower shell of the compressor rubbing against the ground.

[0240] In some embodiments, due to the fixed height of the first shell 11, if 4.5<H16 / H21<6.5, which is beneficial to reduce the noise generated by the compressor vibration, improve the stability of the compressor operation, and avoid the lower shell of the compressor rubbing against the ground.

[0241] In some embodiments, referring to FIG. 1C, when the connecting piece passes through the mounting hole 417, the inner wall of the mounting hole 417 is configured to limit the connecting piece. It should be noted that the inner diameter of the first shell 11 is D14. The inner diameter of the mounting hole 417 is D10.

[0242] In some embodiments, due to the fixed inner diameter of the first shell 11, if 5.5≥D14 / D10, the inner diameter of the mounting hole 417 is too large, the inner wall of the mounting hole 417 cannot limit the connecting piece, which increases the vibration amplitude of the compressor, and the connecting piece is prone to breakage when the compressor is transported.

[0243] In some embodiments, due to the fixed inner diameter of the first shell 11, if 5.5<D14 / D10, as D14 / D10 increases, the inner diameter of the mounting hole 417 decreases, and the inner wall of the mounting hole 417 can limit the connecting piece, which is beneficial to reduce the vibration of the compressor and reduce the noise generated by the vibration of the compressor.

[0244] In some embodiments, due to the fixed inner diameter of the first shell 11, if D14 / D10≥8.5, the inner diameter of the mounting hole 417 is too small, which causes the connecting piece to collide with the inner wall of the mounting hole 417 when the compressor vibrates, and increases the noise.

[0245] In some embodiments, since the inner diameter of the first shell 11 is fixed, if D14 / D10<8.5, as D14 / D10 decreases, the inner diameter of the mounting hole 417 increases, and when the compressor vibrates, since there is a gap between the connecting piece and the inner wall of the mounting hole 417, this is conducive to reducing the vibration of the compressor, and also conducive to reducing noise.

[0246] It should be noted that since the inner diameter of the first shell 11 is fixed, if 5.5

[0247] Any technical disclosure in the present disclosure, and the recombination of multiple technical disclosures can form a complete technical solution, and can solve one or more of the above technical problems, achieve the purpose of disclosure, and belong to the content of the present disclosure, and directly and without doubt determined according to the content of the present disclosure.

[0248] Those skilled in the art will understand that the scope of the disclosure of the present disclosure is not limited to the above specific embodiments, and certain elements of the embodiments can be modified and replaced without departing from the spirit of the present application. The scope of the present application is limited by the appended claims.

Claims

1. A compressor, comprising: a first shell; a compression mechanism arranged in the first shell, the compression mechanism being configured to compress refrigerant; a sensor arranged on a circumferential wall of the first shell, the sensor being configured to acquire a tangential vibration first signal of the first shell; an exciter arranged on the circumferential wall of the first shell, the exciter being configured to emit a second signal of equal amplitude and opposite phase according to the tangential vibration first signal acquired by the sensor to reduce vibration of the compressor. 2.The compressor of claim 1, further comprising a processor configured to receive the tangential vibration first signal acquired by the sensor and transmit the first signal to the exciter after reversing the phase of the first signal by 180°. 3.The compressor of claim 1 or 2, comprising: a compressor body, a height of the body of the compressor is H12; a gas-liquid separator configured to provide gaseous refrigerant into a compression cavity of the compression mechanism, the gas-liquid separator comprising a second shell arranged outside the first shell, an outer diameter of the second shell is D13, a height of the gas-liquid separator is H13; and at least one bracket configured to connect the first shell and the second shell, the bracket being welded to the first shell, an outer diameter of the first shell is D12; wherein the D13 and the D12 satisfy: D13 / D12 ∈ (0.45, 0.56), and the H13 and the H12 satisfy: H13 / H12 ∈ (0.4, 0.6). 4.The compressor of claim 3, wherein: a number of welding points between the bracket and the first shell is n, the D12 and the n satisfy: D12 / n × 10 ∈ (6, 7.5). a number of welding points between the bracket and the first shell is n, the H12 and the n satisfy: H12 / n × 20 ∈ (4.5, 6). 6.The compressor of any one of claims 1 to 5, wherein:

5. The compressor of claim 3 or 4, wherein, the compression mechanism comprises an eccentric crankshaft, at least one cylinder, at least one bearing and a piston, the bearing and the piston being arranged on the eccentric crankshaft, the piston being arranged in a compression cavity of the cylinder; the compressor further comprises a motor, the motor comprising a stator and a rotor, the rotor being sleeved on a first shaft segment of the eccentric crankshaft, a height of the rotor along an axial direction of the eccentric crankshaft is H8, an outer diameter of the rotor is D9; wherein the D14, the H8 and the D9 satisfy: D14 / (H8 × D9) ∈ (0.028, 0.032). 7.The compressor of claim 6, wherein: a height of the shell is H16, a height of the rotor is H8, a gap between the stator and the rotor is S, H16 / (H8 × S) ∈ (6.5, 9.5). 8.The compressor of claim 6 or 7, further comprising an exhaust pipe arranged on a top of the first shell; the compression mechanism further comprises a partition plate, ​ ​ wherein ​ The at least one cylinder comprises a first cylinder and a second cylinder, and the at least one bearing comprises a first bearing and a second bearing; The eccentric crankshaft comprises a first shaft segment, a first eccentric shaft segment, a connecting shaft segment, a second eccentric shaft segment and a second shaft segment connected in sequence, the first bearing is sleeved on the outside of the first shaft segment, the first eccentric shaft segment is located in the first cylinder, the middle partition plate is sleeved on the outside of the connecting shaft segment, the second eccentric shaft segment is located in the second cylinder, the second bearing is sleeved on the outside of the second shaft segment, and the first bearing is fixedly connected with the inner wall of the shell; The compressor comprises an oil equalization pipe, a first end of the oil equalization pipe is connected with the first shell, a second end of the oil equalization pipe is connected with the exhaust pipe, the connection position of the oil equalization pipe and the first shell is lower than the first bearing in the axial direction of the compressor, the distance between the connection position of the oil equalization pipe and the first shell and the bottom of the first shell is H17, the distance between the central axis of the suction port of the first cylinder and the bottom of the first shell is H18, and H17 / H18∈[0.9, 1.2].

9. The compressor of any one of claims 6 to 8, wherein The height of the stator is H19, the outer diameter of the stator is D15, a plurality of convex portions and a plurality of concave portions are arranged on the outer peripheral wall of the stator, the plurality of convex portions are connected with the inner wall of the first shell, the area of the plurality of convex portions is S1, and S1 / π×D15×H19∈[0.35, 0.5]. The bracket comprises a bracket one part, a bracket two part, a bracket three part and a bracket four part connected in sequence, the bracket one part and the bracket three part are located on the same side of the bracket two part, the bracket two part and the bracket four part are located on the different side of the bracket three part, the bracket two part is adapted to and fixedly connected with the outer contour of the second shell, the bracket one part and the bracket three part extend between the first shell and the second shell respectively, the bracket one part and the bracket four part are fixedly connected with the first shell respectively, and the length of the bracket one part is greater than the length of the bracket three part. The at least one bracket comprises two brackets, the two brackets are symmetrically arranged, and any one of the two brackets comprises a bracket four part.

10. The compressor of claims 3-9, wherein, 12. The compressor of claim 10 or 11, wherein 11. The compressor of claims 3-10, wherein, The bracket one part comprises an opening extending in the length direction of the bracket one part, the width of the opening is H14, the length of the opening is L1, and H14 / L1∈(0, 0.82].

13. The compressor of any one of claims 10 to 12, wherein The width of the bracket two part is W3, the radius of the outer contour of the second shell is R2, and W3 / R2∈[1.4, 2.2].

14. The compressor of any one of claims 10 to 13, wherein ​ ​ A distance from a junction of the first bracket part and the second bracket part to a symmetry plane of the two brackets is W1, a distance from the third bracket part to the symmetry plane of the two brackets is W2, an outer contour radius of the second shell is R2, an outer contour radius of the first shell is R1, and (W1 / R2)×(W2 / R1) > 0.

3.

15. The compressor of any one of claims 10 to 14, wherein, The bracket comprises a bracket body part and two bracket extension parts symmetrically arranged at opposite ends of the bracket body part, the bracket body part is adapted to and fixedly connected with an outer contour of the first shell, and each of the two bracket extension parts comprises an extension part one and an extension part two, the extension part one is connected between the bracket body part and the extension part two, and the extension part two is fixedly connected with an outer contour of the second shell.

16. The compressor of claim 15, wherein, An outer contour radius of the first shell is R1, an outer contour radius of the second shell is R2, and a distance between the extension part one and the symmetry plane of the bracket is W4, and 2W4 / (R1+R2) ∈ [0.35, 0.55].

17. The compressor of claim 15 or 16, wherein, A distance between a welding point position between the bracket body part and the first shell and the symmetry plane of the bracket is W5, and W5 / W4 > 0.

75.

18. The compressor of any one of claims 1 to 17, further comprising a damper device configured to carry a compressor body of the compressor, wherein, A height of the first shell is H16, and a height of the damping device is H21, and H16 / H21 ∈ (4.5, 6.5).

19. The compressor of claim 18, further comprising: a mounting part connected with the first shell; a mounting hole provided on the mounting part; and a connecting piece connecting the damping device with the mounting part through the mounting hole; wherein an inner diameter of the mounting hole is D10, an inner diameter of the first shell is D14, and D14 / D10 ∈ (5.5, 8.5).

20. An air conditioner, comprising: an indoor unit, the indoor unit comprising: a first heat exchanger located in the indoor unit and configured to exchange heat with indoor air; and a fan assembly located in the indoor unit and configured to output the heat-exchanged indoor air to an indoor space; an outdoor unit connected with the indoor unit, and further comprising: a second heat exchanger configured to exchange heat with outdoor air; and a compressor, wherein the compressor is any one of claims 1 to 19.

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